EP2913567B1 - Sealing device and rotating machine - Google Patents

Sealing device and rotating machine Download PDF

Info

Publication number
EP2913567B1
EP2913567B1 EP12889652.9A EP12889652A EP2913567B1 EP 2913567 B1 EP2913567 B1 EP 2913567B1 EP 12889652 A EP12889652 A EP 12889652A EP 2913567 B1 EP2913567 B1 EP 2913567B1
Authority
EP
European Patent Office
Prior art keywords
seal
sealing device
swirl
rotary body
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP12889652.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2913567A4 (en
EP2913567A1 (en
Inventor
Kei HASHIZUME
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Compressor Corp
Original Assignee
Mitsubishi Heavy Industries Compressor Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Compressor Corp filed Critical Mitsubishi Heavy Industries Compressor Corp
Publication of EP2913567A1 publication Critical patent/EP2913567A1/en
Publication of EP2913567A4 publication Critical patent/EP2913567A4/en
Application granted granted Critical
Publication of EP2913567B1 publication Critical patent/EP2913567B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/083—Sealings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/08—Sealings
    • F04D29/10—Shaft sealings
    • F04D29/102—Shaft sealings especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/444—Free-space packings with facing materials having honeycomb-like structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/447—Labyrinth packings
    • F16J15/4472—Labyrinth packings with axial path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the present invention relates to a sealing device and a rotating machine.
  • a sealing device which reduces an amount of leakage of a fluid from a clearance between a stationary side and a rotating side between which a differential pressure is present, is typically provided.
  • non-contact type seal As the sealing device, one that is a non-contact type and has high reliability is frequently used.
  • non-contact type seal As a representative non-contact type sealing device (hereinafter referred to simply as “non-contact type seal”), a labyrinth-shaped sealing device has been known.
  • pressure distribution circumferential asymmetrical pressure distribution
  • swirl flow hereinafter referred to simply as “swirl”
  • annular clearance a technique of providing an annular chamber in an outer circumference of a seal ring in order to relieve circumferential pressure distribution in a seal and providing a cavity part causing the annular chamber and a clearance between a stationary body and a rotary body (hereinafter referred to as "seal clearance") to communicate with each other at an interval in a circumferential direction.
  • a damper type sealing device (hereinafter referred to simply as "damper seal") is sometimes used from the viewpoint of giving a damping force exceeding a destabilizing force occurring in the rotating machine.
  • the damper seal includes a packet-shaped sealing device, a honeycomb-shaped sealing device, a hole-pattern-shaped sealing device, and so on. These damper seals can reduce a swirl in the sealing device and obtain a high damping force by partitioning a seal clearance between a seal rotary body and a seal stationary body in a circumferential direction and in an axis direction.
  • Japanese Application 2011-226559 discloses a sealing device according to the preamble of claim 1.
  • the present invention has been made in consideration of the above circumstances and an object of the present invention is to provide a sealing device capable of reducing an amount of leakage, reducing a force from a fluid flowing through a seal clearance responsible for shaft vibration, and increasing damping that suppresses the shaft vibration, and a rotating machine equipped with the sealing device.
  • the seal stationary body is formed with a plurality of holes in an inner surface facing the outer circumferential surface of the seal rotary body, and grooves in a circumferential direction of the inner surface.
  • the seal rotary body has first protrusions that protrude toward the grooves.
  • the grooves in the sealing device of the first aspect may each have an uneven portion configured to disturb the flow of the fluid on at least one of both wall surfaces in a direction of an axis.
  • the flow of the fluid can be disturbed, and a part of the swirl can be blocked.
  • the non-uniformity of the circumferential pressure caused by the swirl can be further reduced.
  • the uneven portion in the sealing device of the first or second aspect may be formed by a part of each of the holes which each of the grooves crosses.
  • the grooves are formed to cross the holes, and thereby the uneven portions can be formed.
  • the uneven portions can be easily formed.
  • the sealing device of any one of the first to third aspects may include a swirl flow prevention mechanism configured to blow the fluid that flows into the clearance between the outer circumferential surface of the seal rotary body and the seal stationary body in a direction against a swirl included in the fluid.
  • the fluid flowing into the clearance between the outer circumferential surface of the seal rotary body and the seal stationary body is blown in the direction against the swirl included in the fluid, and thereby the swirl of the fluid flowing into the clearance between the seal stationary body and the seal rotary body can be counteracted.
  • the swirl flow prevention mechanism of the fourth aspect may include fins that extend toward an outer circumference side of the seal rotary body and passages that lead from outer circumferential portions of the fins to the clearance.
  • the swirl adjacent to the seal rotary body can be guided to and decelerated at the outer circumference side by the fins, and the fluid can be guided to the clearance between the seal rotary body and the seal stationary body via the passages and disturb the flow. An amount of the swirl included in the fluid flowing into the clearance can be reduced.
  • the fins of the swirl flow prevention mechanism of the fourth or fifth aspect may be configured to be inclined in a direction in which a swirl flow is scooped up with respect to the radial direction of the seal rotary body.
  • a greater swirl can be guided to and decelerated at the outer circumference side by the fins, and the fluid can be guided to the clearance between the seal rotary body and the seal stationary body via the passages and disturb the flow.
  • the amount of the swirl included in the fluid flowing to the clearance can be reduced.
  • the swirl flow prevention mechanism of the fifth or sixth aspect may include a cover portion covering the outer circumferential portions of the fins.
  • a pressure of the fluid guided by the fins is recovered by the cover portion, and thereby an amount of the fluid flowing into the passages can be increased.
  • the swirl flow prevention mechanism of any one of the fifth to seventh aspects may include a non-contact seal between Openings of the passages at a side of the clearance and the fins in the direction of the axis.
  • the fluid with the swirl is prevented from flowing into the sealing device in a large quantity, and the fluid flowing in the direction against the swirl can be configured to mainly flow downstream from the non-contact seal.
  • the non-contact seal is provided, and thereby when the fluid having a higher pressure than the fluid upstream from the seal is used for the fluid flowing against the swirl, the fluid flowing against the swirl can be prevented from flowing upstream.
  • the non-contact seal of the eighth aspect may have damping holes in the inner surface facing the outer circumferential surface of the seal rotary body.
  • the swirl included in the fluid flowing into the clearance from the high pressure side can be reduced between the fins and the openings of the passages at the side of the clearance by the damping holes.
  • the sealing device of any one of the first to ninth aspects may include a second protrusion, which disturbs the flow of the fluid before the fluid flows into the clearance, at a higher pressure side than the seal stationary body on the outer circumferential surface of the seal rotary body.
  • the swirl flow prevention mechanism is provided at the high pressure side of the seal stationary body, the fluid disturbing the flow at the second protrusion is supplied to the swirl flow prevention mechanism, and can be effectively used as the fluid blown by the swirl flow prevention mechanism.
  • the seal stationary body in the sealing device of any one of the first to tenth aspects may include narrow passages that communicate with the holes and has a narrower flow passage area than the holes, and annular passages with which some of the narrow passages communicate and which are disposed on an outer circumference side of the holes.
  • a rotating machine according to the present invention includes the sealing device of any one of the first to eleventh aspects.
  • the sealing device and the rotating machine relating to the above aspects of the present invention, the flow of the fluid flowing through the seal clearance is greatly disturbed, and the amount of the swirl is reduced. Thereby, it is possible to reduce the amount of leakage, to reduce the force from the fluid flowing through the seal clearance responsible for the shaft vibration, and to increase the damping that suppresses the shaft vibration.
  • Fig. 1 illustrates a centrifugal compressor 1 that is the rotating machine of the present embodiment.
  • the centrifugal compressor 1 is equipped with a rotating shaft 2 rotating about an axis O. Multiple impellers 3 compressing a process gas (fluid) G using a centrifugal force are mounted on the rotating shaft 2. Also, the centrifugal compressor 1 is equipped with a casing 5 having a flow passage 4 causing the process gas G to flow from a low pressure side to a high pressure side.
  • Each end of the casing 5 in a direction of the axis O is provided with a shaft sealing device 5a, a journal bearing 5b, and a thrust bearing 5c. Both ends of the rotating shaft 2 are rotatably supported on the casing 5 by the journal bearings 5b.
  • Impellers 3 of the centrifugal compressor 1 in the present embodiment constitute two impeller groups 3A and 3B whose blades turn to sides opposite to each other in the direction of the axis O of the rotating shaft 2.
  • the impeller group 3A and the impeller group 3B compress the process gas G from suction ports 5d and 5f toward discharge ports 5e and 5g, respectively, while causing the process gas G to flow.
  • the centrifugal compressor 1 causes the process gas G suctioned from the suction port 5d to flow into the flow passage 4 in the impeller group 3A, and compresses the process gas G while causing the process gas G to flow from a first stage of the impeller group 3A to a third stage.
  • the process gas G compressed by flowing to the third stage of the impeller group 3A is discharged from the discharge port 5e.
  • the process gas G discharged from the discharge port 5e is sent to the suction port 5f through a pipeline (not shown) connected from the discharge ports 5e to the suction port 5f.
  • the centrifugal compressor 1 causes the process gas G suctioned from the suction port 5f to flow into the flow passage 4 in the impeller group 3B, and further compresses the process gas G while causing the process gas G to flow from a first stage of the impeller group 3B to a final stage.
  • the process gas G compressed by flowing to the final stage of the impeller group 3B is discharged from the discharge port 5g.
  • the process gas G adjacent to the discharge port 5g of the aforementioned impeller group 3B has a high pressure in proportion to the extent to which it is compressed by the impeller group 3B. That is, a pressure difference occurs between the process gas G present in the around of the rotating shaft 2 at the side of the discharge port 5e in the direction of the axis O and the process gas G present in the around of the rotating shaft 2 at the side of the discharge port 5g in the direction of the axis O.
  • the sealing device 20 by which the high pressure side and the low pressure side are sectioned off in the direction of the axis O of the rotating shaft 2 and which reduces an amount of leakage of the process gas G while allowing of the rotation of the rotating shaft 2, is provided between the final stages of the impellers 3 of the impeller groups 3A and 3B.
  • Fig. 2 is a perspective view illustrating a partial cross section of a seal stationary body 30 constituting the sealing device 20.
  • Fig. 3 is a meridian sectional view of an upper portion of the sealing device 20.
  • a seal rotary body 40 that is an approximately annular sleeve is fixed to the rotating shaft 2 so as to cover an outer circumferential surface of the rotating shaft 2.
  • the seal stationary body 30 having an approximately annular shape is mounted on an inner circumferential surface 5h of the casing 5 which faces the outer circumferential surface 2a of the rotating shaft 2 with a clearance from an outer circumferential surface 40a of the seal rotary body 40 in a radial direction.
  • the seal stationary body 30 is fixed, for instance, in such a manner that an engagement protrusion 30c thereof is engaged with an engagement recess 5i formed in an inner circumferential surface of, for instance, the casing 5 or a partition plate (not shown).
  • the seal stationary body 30 is a so-called damping seal ring having a hole pattern, and an inner circumferential surface 30a thereof is formed with a plurality of holes 31 that are open toward a radial inner side in a circular shape. Openings 31a of these holes 31 are disposed at predetermined intervals from each other in a zigzag pattern.
  • the basic arrangement of the holes 31 in the inner circumferential surface 30a of the seal stationary body 30 is shown in Fig. 4 .
  • a leftward/rightward direction is equivalent to the direction of the axis O of the seal stationary body 30, and an upward/downward direction is equivalent to the circumferential direction of the seal stationary body 30.
  • positions at which grooves 32 to be described below are formed are shown by a line composed of alternating long and short dashes.
  • the inner circumferential surface 30a of the seal stationary body 30 is formed with annular grooves 32 having a predetermined width in the direction of the axis O.
  • These grooves 32 are recessed from the inner circumferential surface 30a toward a radial outer side, and are each formed to cross the holes 31 formed in the seal stationary body 30 in the circumferential direction.
  • portions recessed toward both outer sides in the direction of the axis O in a circular arc shape in a cross section are intermittently formed in two sidewalls 32a of each groove 32 which face each other in the direction of the axis O, and thereby uneven portions 32b are formed on the sidewalls 32a.
  • a leftward/rightward direction is equivalent to the direction of the axis O of the seal stationary body 30, and an upward/downward direction is equivalent to the circumferential direction of the seal stationary body 30.
  • the width of each groove 32 is a width greater than an allowable movement amount of the rotating shaft 2 in the direction of the axis O such that each of first protrusions 34 of the seal rotary body to be described below and the sidewalls 32a of each groove 32 do not come into contact with each other, and may be a width dimension that the uneven portions 32b are formed on the sidewalls 32a. Also, the uneven portions 32b have been described as being formed on the sidewalls 32a. However, when the holes 31 are disposed within the width of each groove 32, the openings 31a of the holes 31 are also formed in the bottom of each groove 32.
  • Each of the first protrusions 34 is formed on the outer circumferential surface 40a of the seal rotary body 40 which faces the inner circumferential surface 30a of the seal stationary body 30 throughout the circumference of the radial outer side so as to protrude toward each groove 32 of the seal stationary body 30.
  • a width dimension of the first protrusion 34 need only be necessary and sufficient in view of strength, and a height of the first protrusion 34 may also be a height (e.g., similar to or somewhat higher than the seal clearance S) required to disturb the flow of the fluid leaking from the seal clearance.
  • narrow passages 35 are connected to each predetermined number of holes 31 in the seal stationary body 30 among the holes 31 arranged in the direction of the axis O.
  • the narrow passages 35 extend from the bottoms 31b of the holes 31 to the radial outer side, and are formed to have circumferential cross sections (in other words, flow passage areas) smaller than those of the holes 31.
  • the circumferential cross sections of the narrow passages 35 have an adequate size in consideration of the conditions of use.
  • annular passages 36 are formed at the radial outer side (outer circumference side) of the narrow passages 35 throughout the circumference of the seal stationary body 30.
  • the plurality of narrow passages 35 aligned in the circumferential direction are connected to the annular passages 36 from the radial inner side. In this way, the narrow passages 35 and the annular passages 36 are connected, and thereby internal flow passages of the holes 31 and the annular passages 36 communicate with each other via the narrow passages 35.
  • the narrow passages 35 and the annular passages 36 may, for instance, be formed by forming the annular passages 36, the narrow passages 35, and the holes 31 with separate parts and coupling the parts to each other.
  • the seal stationary body 30 is provided with a swirl flow prevention mechanism 37 at the high pressure side thereof.
  • the swirl flow prevention mechanism 37 blows the process gas G in a direction against a swirl (swirl flow).
  • the direction against the swirl is any direction between the radial direction and the circumferential direction that becomes a direction opposite to the direction of rotation.
  • the swirl flow prevention mechanism 37 is equipped with a plurality of fins 38 in approximately rectangular plate shapes. These fins 38 are obliquely provided such that short sides 38a thereof are directed in the direction of the axis O and long sides 38b scoop up the swirl in a swirling direction of the process gas G rather than the radial direction. Further, the swirl flow prevention mechanism 37 is equipped with openings 39a at a radial outer portion (outer circumferential portion) of the low pressure side relative to the fins 38. Radial outer ends of blowoff passages 39b that extend toward the radial inner side after being directed in the direction of the axis O are connected to these openings 39a.
  • blowoff passages 39b face the seal clearance S between the inner circumferential surface 30a of the seal stationary body 30 and the outer circumferential surface 40a of the seal rotary body 40 and are connected to openings 39c directed in the direction against the swirl.
  • a second protrusion 42 is formed on the outer circumferential surface 40a of the seal rotary body 40 mounted on the rotating shaft 2 at a position that becomes a higher pressure side than the seal stationary body 30 in the direction of the axis O in order to disturb the flow of the process gas G.
  • the second protrusion 42 is disposed adjacent to the fins 38.
  • the second protrusion 42 is continuously formed in the circumferential direction, and has a height that is at least equal to a distance between the short side 38a of the inner circumferential side of each fm 38 and the outer circumferential surface 40a of the seal rotary body 40.
  • a portion of the process gas G that disturbs the flow by providing the second protrusion 42 can be caused to flow along the aforementioned fins 38 toward the radial outer side.
  • the swirl included in the process gas G generated by the rotary body such as the rotating shaft 2 or the impeller 3 is enlarged in the vicinity of the rotary body.
  • the swirl is reduced in the vicinity of the stationary body due to a frictional loss of a wall surface of the stationary body. That is, it is possible to guide most of the swirl adjacent to the rotating shaft 2 to the vicinity of the stationary body disposed at the radial outer side of the rotating shaft 2 by the fins 38, and the swirl can be decelerated. Thereby, an amount of the swirl of the process gas G flowing into the seal clearance S can also be reduced.
  • Labyrinth fins 39d protrude from the inner circumferential surface 30a of the seal stationary body 30 toward the radial inner side between the fins 38 and the openings 39c in the direction of the axis O.
  • the labyrinth fins 39d are continuously formed in the circumferential direction of the inner circumferential surface 30a of the seal stationary body 30. Due to the labyrinth fins 39d, the seal clearance S between the inner circumferential surface 30a of the seal stationary body 30 and the outer circumferential surface 40a of the seal rotary body 40 is partly narrowed. Thereby, an amount of the process gas flowing into the seal clearance S is reduced, and a pressure difference between high and low pressure sides of the labyrinth fins 39d is maintained.
  • a pressure of the low pressure side becomes a pressure at which an amount of leakage of the damping seal (the seal stationary body 30 and the seal rotary body 40) downstream from the blowoff passages 39b and the labyrinth fins 39d balances an amount of leakage of the labyrinth fins 39d and an amount of blowoff from the blowoff passages 39b. That is, the process gas G is set to be blown off from the blowoff passages 39b to the low pressure side of the labyrinth fins 39d using a pressure difference between a static pressure of the process gas G of an outer diameter portion of the aforementioned fins 38 and a pressure of the low pressure side of the aforementioned fins 38.
  • annular cover part 50 may be mounted to cover the radial outer portion of the fins 38 from the high pressure side.
  • the sealing device 20 of the aforementioned embodiment when the process gas G flows along the seal clearance S between the seal stationary body 30 and the seal rotary body 40 from the high pressure side toward the low pressure side, the flow in the direction of the axis O and the circumferential direction is greatly disturbed together by the first protrusions 34, the grooves 32, and the holes 31. For this reason, the flow causes great resistance to the flow of the process gas G, and suppresses the swirl of the process gas G flowing along the seal clearance S, and it is possible to reduce the amount of leakage and increase the damping.
  • the grooves 32 are formed to cross the holes 31, and thereby the uneven portions 32b can be formed on the sidewalls 32a of each groove 32.
  • the uneven portions 32b can be easily formed.
  • the process gas G is blown against the process gas G flowing into the seal clearance S in the direction against the swirl by the swirl flow prevention mechanism 37, and thereby the amount of the swirl can be reduced.
  • flowing of the swirl of the process gas G flowing into the seal clearance S between the seal stationary body 30 and the seal rotary body 40 can be counteracted.
  • the swirl of the vicinity of the seal rotary body 40 can be guided to the outer circumference side and decelerated by the fins 38 of the swirl flow prevention mechanism 37, the process gas G is guided to the seal clearance S via the blowoff passages 39b and disturbs the flow, and the amount of the swirl included in the process gas G flowing to the seal clearance S can be reduced.
  • the fins 38 are inclined in the direction in which they scoop up the swirl with respect to the radial direction. Thereby, a greater swirl can be guided to the outer circumference side and decelerated by the fins 38.
  • the labyrinth fins 39d are provided in the direction of the axis O between the openings 39c of the blowoff passages 39b which are at the side of the seal clearance S and the fins 38. Thereby, the process gas G with the swirl can be prevented from flowing into the seal clearance S in a large quantity, and the process gas G flowing in the direction against the swirl can be made to mainly flow downstream from the labyrinth fins 39d.
  • the labyrinth fins 39d are provided. Thereby, when a process gas G having a higher pressure than a fluid pressure upstream from the seal is used for the process gas G flowing against the swirl, the process gas G flowing against the swirl can be prevented from flowing upstream.
  • the swirl flow prevention mechanism 37 is provided at the high pressure side of the seal stationary body 30, the process gas G whose flow is disturbed by the second protrusion 42 is supplied to the swirl flow prevention mechanism 37, and can be effectively used as the process gas G blown by the swirl flow prevention mechanism 37.
  • centrifugal compressor 1 of this embodiment it is possible to suppress the swirl of the process gas G, reduce the amount of leakage, and increase the damping, and thus it is possible to improve running performance.
  • the present invention is not limited to the aforementioned embodiment, and includes various ways of modifying the aforementioned embodiment without departing from the spirit and scope of the present invention. That is, the specific shape and constitution represented in the embodiment are merely examples and can be appropriately modified.
  • sealing device 20 may be divided and installed in the direction of the axis O.
  • the sealing device 20 may be installed at multiple places in the centrifugal compressor 1 that is the rotating machine.
  • the seal rotary body 40 on which the first protrusions 34 are formed and which has a circular pipe is mounted on the rotating shaft 2 has been described.
  • the first protrusions 34 may be formed on the outer circumferential surface 2a of the rotating shaft 2, and the rotating shaft 2 may be used as the seal rotary body.
  • the arrangement of the holes 31 is not limited to the zigzag shape, and may be, for instance, a square arrangement.
  • the seal stationary body 30 having the hole pattern shape has been described by way of example.
  • the seal stationary body 30 may be a seal stationary body that has holes demarcated in the circumferential direction and in the direction of the axis O and can apply a damping force, and may be a seal stationary body having a pocket shape or a honeycomb shape. Even when the seal stationary body having the pocket shape or the honeycomb shape is used, similar to the seal stationary body 30 having the hole pattern shape, the grooves 32 are formed in the circumferential direction of the seal stationary body and are formed to cross the holes 31. Thereby, the uneven portions 32b can be formed on the sidewalls 32a.
  • the uneven portions 32b are formed on both of the sidewalls 32a in the direction of the axis O of each groove 32 has been described.
  • the uneven portions 32b may be formed on any one of the sidewalls 32a.
  • the uneven portions 32b formed on the sidewalls 32a of each groove 32 may be omitted. Even in this case, the flow of the process gas G is disturbed by the grooves 32, the first protrusions 34, and the holes 31, and the swirl included in the process gas G can be reduced.
  • the swirl flow prevention mechanism 37 is provided at the high pressure side relative to the seal stationary body 30 .
  • the swirl flow prevention mechanism 37 may be provided at an intermediate portion of the seal stationary body 30.
  • the swirl flow prevention mechanism 37 may be provided or omitted according to necessity.
  • the narrow passages 35 and the annular passages 36 are formed has been described.
  • the narrow passages 35 and the annular passages 36 may be omitted when the swirl caused by the rotation of, for instance, the rotating shaft 2 is reduced.
  • the uneven portions 32b may be adapted to be formed on the sidewalls 32a of each groove 32 by methods other than cutting. For example, a process of recessing the sidewalls 32a of each groove 32 in the direction of the axis O may be performed, or a process of protruding inward from the sidewalls 32a of each groove 32 in the direction of the axis O may be performed.
  • the holes 31 are also formed in the bottoms of the grooves 32 facing the first protrusions 34 , but the holes 31 are not necessarily provided.
  • the number of holes 31 formed in the bottoms of the grooves 32 need only be set to a proper number corresponding to desired seal performance, and may, for example, be smaller than the number of holes 31 of the seal stationary body 30 other than the grooves 32 in the circumferential direction.
  • the second protrusion 42 may be omitted according to a state of the swirl at the high pressure side of the sealing device 20.
  • the swirl flow prevention mechanism 37 may have a plurality of damping holes 45 formed in an inner surface facing the outer circumferential surface of the seal rotary body between the openings 39c of the blowoff passages (paths) 39b which are at the side of the seal clearance S and the fins 38 in the direction of the axis O.
  • the damping holes 45 have the same constitution as the aforementioned holes 31. The swirl included in the process gas G flowing from the high pressure side into the seal clearance S between the fins 38 and the openings 39c of the blowoff passages 39b which are at the side of the seal clearance S can be reduced by the damping holes 45.
  • the number of rows of the damping holes 45 in the direction of the axis O is not limited to that of Fig. 10 , and the damping holes 45 may be formed in at least one row.
  • another non-contact seal for instance, a pocket-shaped or honeycomb-shaped non-contact seal
  • the present invention may be applied as a sealing device that reduces a flow of a fluid on an outer circumferential surface of a rotary body in a direction of an axis or a sealing device that adds damping in order to improve a vibration-resistant force of a rotor.
  • the present invention may be applied to a rotating machine equipped with the sealing device.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
EP12889652.9A 2012-12-06 2012-12-06 Sealing device and rotating machine Not-in-force EP2913567B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/081618 WO2014087512A1 (ja) 2012-12-06 2012-12-06 シール装置、および、回転機械

Publications (3)

Publication Number Publication Date
EP2913567A1 EP2913567A1 (en) 2015-09-02
EP2913567A4 EP2913567A4 (en) 2015-10-21
EP2913567B1 true EP2913567B1 (en) 2016-10-19

Family

ID=50882962

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12889652.9A Not-in-force EP2913567B1 (en) 2012-12-06 2012-12-06 Sealing device and rotating machine

Country Status (5)

Country Link
US (1) US20150337851A1 (ja)
EP (1) EP2913567B1 (ja)
JP (1) JP5922796B2 (ja)
CN (1) CN104813082B (ja)
WO (1) WO2014087512A1 (ja)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10066750B2 (en) * 2012-11-13 2018-09-04 Mitsubishi Heavy Industries Compressor Corporation Rotary machine
JP2016089856A (ja) * 2014-10-29 2016-05-23 三菱重工業株式会社 シール装置及び回転機械
EP3034784A1 (de) * 2014-12-19 2016-06-22 Siemens Aktiengesellschaft Kühlmöglichkeit für strömungsmaschinen
DE102015104994A1 (de) * 2015-03-31 2016-10-06 Areva Gmbh Dichtungsanordnung für eine drehbeweglich gelagerte Komponente einer Rotationsmaschine
US10718346B2 (en) * 2015-12-21 2020-07-21 General Electric Company Apparatus for pressurizing a fluid within a turbomachine and method of operating the same
JP2017160861A (ja) * 2016-03-10 2017-09-14 株式会社日立製作所 ターボ機械
JP2018053952A (ja) * 2016-09-27 2018-04-05 三菱重工コンプレッサ株式会社 シール機構、回転機械
JP2019161798A (ja) * 2018-03-09 2019-09-19 本田技研工業株式会社 回転電機の冷却構造体
CN110332016B (zh) * 2019-06-24 2021-05-28 西安交通大学 一种能够增强密封性能的孔型密封结构
CN113775762A (zh) * 2021-08-25 2021-12-10 浙江工业大学 一种带燕尾导流槽的孔型阻尼密封结构
CN113775763B (zh) * 2021-08-25 2024-03-26 浙江工业大学 一种孔深可变分瓣式气囊支承孔型阻尼密封

Family Cites Families (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2159766A (en) * 1938-04-15 1939-05-23 Gen Electric Labyrinth packing
US4199154A (en) * 1976-07-28 1980-04-22 Stauffer Chemical Company Labyrinth sealing system
JPS58191374A (ja) * 1982-04-30 1983-11-08 Mitsubishi Heavy Ind Ltd 軸封装置
JPH0660692B2 (ja) * 1986-02-27 1994-08-10 三菱重工業株式会社 回転機械のシ−ル装置
JPS63110771U (ja) * 1987-01-13 1988-07-16
JPH0311178U (ja) * 1989-06-21 1991-02-04
US6091568A (en) * 1998-02-17 2000-07-18 International Business Machines Corporation Labyrinth seal for minimizing flow gradients leading to aerosoling of contaminants external to spindles
US6155778A (en) * 1998-12-30 2000-12-05 General Electric Company Recessed turbine shroud
JP2001123803A (ja) * 1999-10-21 2001-05-08 Toshiba Corp シール装置並びに同装置を備えた蒸気タービン及び発電プラント
US6350102B1 (en) * 2000-07-19 2002-02-26 General Electric Company Shroud leakage flow discouragers
US6499742B1 (en) * 2001-08-20 2002-12-31 General Electric Company Brush seal assembly and method of using brush seal assembly
US7066470B2 (en) * 2001-12-05 2006-06-27 General Electric Company Active seal assembly
US20040046327A1 (en) * 2002-09-05 2004-03-11 Menendez Robert P. Labyrinth/brush seal combination
US20040239040A1 (en) * 2003-05-29 2004-12-02 Burdgick Steven Sebastian Nozzle interstage seal for steam turbines
WO2004113770A2 (en) * 2003-06-20 2004-12-29 Elliott Company Swirl-reversal abradable labyrinth seal
US20080080972A1 (en) * 2006-09-29 2008-04-03 General Electric Company Stationary-rotating assemblies having surface features for enhanced containment of fluid flow, and related processes
US7748945B2 (en) * 2006-12-07 2010-07-06 Jerry Wayne Johnson Floating sealing ring
SE531210C2 (sv) * 2007-05-07 2009-01-20 Roplan Internat Ab Mekanisk tätningsanordning samt pump
EP2083200A1 (en) * 2008-01-24 2009-07-29 Siemens Aktiengesellschaft Seal assembly
JP2011226559A (ja) * 2010-04-20 2011-11-10 Mitsubishi Heavy Ind Ltd 被切削性ハニカムシール材及びガスタービン
US20120027582A1 (en) * 2010-08-02 2012-02-02 General Electric Company Floating packing ring assembly
JP2012102831A (ja) 2010-11-12 2012-05-31 Hitachi Ltd ラビリンスシール装置、およびそれを用いたターボ機械
IT1403222B1 (it) 2010-12-30 2013-10-17 Nuovo Pignone Spa Sistemi e metodi per rastremazione del rompi-vortice
WO2012129475A2 (en) * 2011-03-24 2012-09-27 Dresser-Rand Company Interlocking hole pattern seal

Also Published As

Publication number Publication date
EP2913567A4 (en) 2015-10-21
WO2014087512A1 (ja) 2014-06-12
JPWO2014087512A1 (ja) 2017-01-05
CN104813082A (zh) 2015-07-29
US20150337851A1 (en) 2015-11-26
JP5922796B2 (ja) 2016-05-24
EP2913567A1 (en) 2015-09-02
CN104813082B (zh) 2016-12-07

Similar Documents

Publication Publication Date Title
EP2913567B1 (en) Sealing device and rotating machine
EP2899405B1 (en) Rotary machine
JP6283351B2 (ja) らせん形およびらせん形−円筒形混合パターンを有する高減衰ラビリンスシール
KR102020138B1 (ko) 라비린스 시일
WO2016079781A1 (ja) ターボ機械
CN104154042B (zh) 用于轴流式涡轮机的抽气系统
JP2014074360A (ja) 遠心圧縮機
EP2154380B1 (en) Seal device for rotary fluid machine and rotary fluid machine
CN109690050B (zh) 轴承构造及增压器
US20070069477A1 (en) Stepped labyrinth damper seal
WO2012001997A1 (ja) シール装置及びこれを備えた流体機械
WO2016043090A1 (ja) 回転機械
JP6418331B2 (ja) 軸受構造、および、過給機
JP6571257B2 (ja) シール装置及びターボ機械
JP2014084803A (ja) 遠心式流体機械
EP2305957B1 (en) Improved staggered seal assembly
WO2017146136A1 (ja) シール装置及び回転機械
US11519287B2 (en) Rotating machine
JP5694128B2 (ja) 蒸気タービン
WO2018110695A1 (ja) 軸シール装置、及び回転機械
JP5364426B2 (ja) ターボ機械
JP7468696B2 (ja) 軸受および過給機
US20210172529A1 (en) Floating ring seal
KR20210128272A (ko) 유체 기계
WO2018123309A1 (ja) ターボチャージャ

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150527

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RA4 Supplementary search report drawn up and despatched (corrected)

Effective date: 20150918

RIC1 Information provided on ipc code assigned before grant

Ipc: F16J 15/44 20060101AFI20150914BHEP

Ipc: F16J 15/40 20060101ALI20150914BHEP

Ipc: F04D 29/08 20060101ALI20150914BHEP

Ipc: F16J 15/447 20060101ALI20150914BHEP

Ipc: F04D 29/10 20060101ALI20150914BHEP

Ipc: F04B 39/00 20060101ALI20150914BHEP

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F16J 15/40 20060101ALI20160408BHEP

Ipc: F04D 17/12 20060101ALI20160408BHEP

Ipc: F04D 29/08 20060101ALI20160408BHEP

Ipc: F16J 15/44 20060101AFI20160408BHEP

Ipc: F04D 29/10 20060101ALI20160408BHEP

Ipc: F04B 39/00 20060101ALI20160408BHEP

Ipc: F16J 15/447 20060101ALI20160408BHEP

INTG Intention to grant announced

Effective date: 20160504

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 838641

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161115

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602012024489

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20161019

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 838641

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161019

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170120

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170119

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170220

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170219

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602012024489

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170119

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

26N No opposition filed

Effective date: 20170720

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20170119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161231

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161206

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161231

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170119

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161206

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20171113

Year of fee payment: 6

Ref country code: DE

Payment date: 20171129

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20121206

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20171221

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20161206

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 602012024489

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190702

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181206

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20181231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20161019